CN1247881C - Arrangement and method for valve control of reversible diesel combustion engine - Google Patents
Arrangement and method for valve control of reversible diesel combustion engine Download PDFInfo
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- CN1247881C CN1247881C CNB981213561A CN98121356A CN1247881C CN 1247881 C CN1247881 C CN 1247881C CN B981213561 A CNB981213561 A CN B981213561A CN 98121356 A CN98121356 A CN 98121356A CN 1247881 C CN1247881 C CN 1247881C
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- Prior art keywords
- valve
- cam
- control
- fuel
- valve cam
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/02—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for reversing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34446—Fluid accumulators for the feeding circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Fuel-Injection Apparatus (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
A structure for controlling a valve for a reversible diesel engine comprises a control shaft 2 provided with at least one fuel cam 4 positively and reversely running in two directions to control fuel injection and at least one valve cam 3 to control the valve for the diesel engine. The valve cam 3 controls opening of the valve 5. A means different from the valve cam 3 is provided to control closing the valve 5.
Description
Technical field
The present invention relates to be used in the reversible diesel machine apparatus and method of valve control.
Background technique
In the reversible diesel machine, particularly for example be used in the large-scale diesel engine of shipbuilding industry, fuel is sprayed and the control of the valve (exhaust and/or suction valve) of cylinder is finished by a Control Shaft, on this axle, be provided with a fuel cam for each cylinder, spray in order to control fuel, and each valve is provided with a valve cam, in order to control this valve.This is controlled at here by the bent axle transmission, and fuel then activates the actuator that links to each other with them with valve cam, and for example, jet pump or elevator pump, these pumps are used for that fuel sprays or the hydraulic actuating of valve.In order will when the internal combustion engine bidirectional (promptly rotating and reverse) that can reverse rotates, to spray and to provide identical condition for itself and the actuating of valve match for fuel, certain measure is taked in requirement, this be because, in general, fuel cam and for example be used for the angular displacement on Control Shaft between the valve cam of outlet valve, as long as two cams can not be located on this Control Shaft movably, be also inequality then to the both direction that rotates.
If for example being used for the valve cam of fuel and outlet valve settles in such a way, promptly lag behind the crankangle on one 140 ° on fuel cam summit when the summit of exhaust-valve cam between the positive refunding, so, the result that opposite direction rotates (counter-rotating) is the crankangle that the summit of exhaust-valve cam lags behind one 215 ° on fuel cam summit, thereby consistent when just changeing no longer of the continuity (referring to the moving period of piston in cylinder) between the actuating of fuel injection and outlet valve.Such result is that the ride quality of internal-combustion engine can be subjected to very big infringement when counter-rotating.
Therefore proposed among German patent DE-A-3128332 when the counter-rotating operation, the fuel cam is rotated with respect to Control Shaft, the fuel cam can be reorientated in the position, angle of Control Shaft between the two positions with regard to them in other words, and outlet valve then still remains on the same angular positions with respect to control valve the rotation of both direction.Can guarantee that by this measure the time point of being controlled all belongs to desirable to two sense of rotation.Being reversed in wherein of fuel cam undertaken by the hydraulic pressure rotating machinery, and the hydraulic pressure rotating machinery makes the fuel cam put to positive transposition to backward position or from backward position from the position of just changeing with respect to Control Shaft and rotates.
Though it is very good that this embodiment proves function, it is too complicated by comparison and expense is big.Therefore because each rotating machinery can only rotate two fuel cams, to cylinder at least one such rotating machinery and desired in each case supply line must be set on Control Shaft for each of internal-combustion engine.Herein, these commutating devices have increased desired amount of space.On the one hand the fuel cam and on the other hand in it device the housing of Control Shaft is arranged, for example, fuel pump housing must make very big.
Summary of the invention
Therefore, from this prior art, one object of the present invention is exactly to propose a kind of simple mechanism that is used for the valve control of reversible diesel machine, wherein to be designed to be with regard to its size be to save the space to Control Shaft, and it also can rotate the both direction of relevant fuel-injected Control Shaft and exercise similar basically valve control.This device should simply and with less complexity and expense be realized on its equipment and structure.In addition, an object of the present invention is to propose a kind of corresponding method, be used for the valve control of the outlet valve and/or the suction valve of reversible diesel machine.
At above-mentioned purpose, the invention provides the device that is used for valve control in a kind of reversible diesel machine, this device comprises that one can be reversed and rotary Control Shaft on both direction, Control Shaft is provided with at least one fuel cam, be used to control the injection of fuel oil, with at least one valve cam, be used to control a valve of diesel engine, this valve cam is being controlled the unlatching of valve, it is characterized in that, also be provided with the other device that is different from valve cam of closing in order to control valve, described fuel cam 4 and valve cam 3 all are mounted to respect to Control Shaft 2 has fixing position, wherein valve cam 3 is installed by this way and is designed, i.e. the unlatching of valve 5 is taking place with respect to fuel injection certain crank angle KW displacement, and this rotation to the both direction of Control Shaft 2 all is identical basically.
The method that is used for valve control in a kind of reversible diesel machine also is provided, comprise the steps: in this internal-combustion engine, to be provided with a Control Shaft that can on both direction, rotate, at least one fuel cam is set on axle is used to control the injection of fuel oil and the valve that at least one valve cam is used to control diesel engine, make this diesel engine rotate with first operator scheme and in second operator scheme, be rotated with the commutation operation along a direction, unlatching by the valve cam control valve, it is characterized in that, by being different from other device the closing of control valve of valve cam, described fuel cam 4 and valve cam 3 all are mounted to respect to Control Shaft 2 has fixing position, wherein valve cam 3 is installed by this way and is designed, the unlatching that is valve 5 is taking place with respect to fuel injection certain crank angle KW displacement, and this rotation to the both direction of Control Shaft 2 all is identical basically.
In addition, a kind of reversible diesel machine is provided, the device that is used for valve control in this diesel engine comprises that one can be reversed and rotary Control Shaft on both direction, Control Shaft is provided with at least one fuel cam, be used to control the injection of fuel oil, with at least one valve cam, be used to control a valve of diesel engine, this valve cam is being controlled the unlatching of valve, it is characterized in that, also be provided with the other device that is different from valve cam of closing in order to control valve, described fuel cam 4 and valve cam 3 all are mounted to respect to Control Shaft 2 has fixing position, wherein valve cam 3 is installed by this way and is designed, i.e. the unlatching of valve 5 is taking place with respect to fuel injection certain crank angle KW displacement, and this rotation to the both direction of Control Shaft 2 all is identical basically.
Have again, a kind of operation method of reversible diesel machine is provided, comprise the steps: in this internal-combustion engine, to be provided with a Control Shaft that can on both direction, rotate, at least one fuel cam is set on axle is used to control the injection of fuel oil and the valve that at least one valve cam is used to control diesel engine, make this diesel engine rotate with first operator scheme and in second operator scheme, be rotated with the commutation operation along a direction, unlatching by the valve cam control valve, it is characterized in that, by being different from other device the closing of control valve of valve cam, described fuel cam 4 and valve cam 3 all are mounted to respect to Control Shaft 2 has fixing position, wherein valve cam 3 is installed by this way and is designed, the unlatching that is valve 5 is taking place with respect to fuel injection certain crank angle KW displacement, and this rotation to the both direction of Control Shaft 2 all is identical basically.
Therefore, according to the present invention, a valve cam on Control Shaft is being controlled the unlatching of valve, and closing then of valve controlled by the device different with valve cam.By this measure, only require a side that utilizes the valve cam side for each sense of rotation, because the control of closing for valve is provided with other device in addition rather than uses particularly second side of valve cam.Therefore, valve cam can be arranged and design in such a way, in a desirable mode and with respect to the desirable time point of fuel-injected the unlatching of valve is being controlled, these functions during reversing then are responsible in its second side between the positive refunding in a side that makes it.
So just no longer need when the counter-rotating operation, rotate fuel cam or valve cam separately.This means at equipment and structural cost and complexity and reduce greatly, and needn't make any compromise in the ideal time that activates about fuel injection and valve on the order one of both direction of rotating.Because independent cam is no longer needed commutating device, independent cam can directly be contained on the Control Shaft in each case thereby can make less.The result is, accommodates the shell of associated actuator, and for example, the fuel pump shell also can be made littler and more compact.
Device of the present invention and method of the present invention for example are specially adapted to two-stroke large-scale diesel engine used in shipbuilding industry separately.
Description of drawings
With the content of one exemplary embodiment the present invention is described in detail below with reference to accompanying drawings with regard to equipment and method two aspects.Be not in the pro rata schematic representation, parts identical or that have said function all are marked with identical label, in the accompanying drawing:
Fig. 1 is first embodiment's of apparatus of the present invention a critical piece, and part illustrates with sectional view,
Fig. 2 is device and operating method of apparatus of the present invention and/or the chart of the inventive method in order to the explanation cam,
Fig. 3 is the sectional view of a valve cam,
Fig. 4 be a variant of valve cam sectional view and
Fig. 5 is that a symbol of one second one exemplary embodiment of the present invention explains orally schematic diagram.
Embodiment
Below about in the description of the invention, proposed a kind of by way of example as be used for having of shipbuilding industry of longitudinally scavenged two-stroke large-scale diesel engine, the outlet valve of one of them cylinder as an example as controlled valve.Certainly the present invention also can be applicable to the valve control of suction valve in a similar fashion.Because it is enough for understanding purport of the present invention, therefore is only limited to a cylinder in explanation, just, the outlet valve of this cylinder." fuel cam " and " valve cam " are understood to mean those cams of both and this cylinder associated hereinafter; That is to say that the fuel cam is to be connected in mutually on the same cylinder with valve cam.Not saying self-evident is under the situation of a plurality of cylinders, and each cylinder respectively is equipped with a fuel cam and a valve cam, as described hereinafter.
Fig. 1 demonstrates one first embodiment's of apparatus of the present invention diagram, and this device is used for the valve control of a reversible diesel machine (not giving more detailed demonstration).This device is generally with label 1 representative.It comprises a complete reversible Control Shaft 2, and this can rotate on both direction and drive with the bent axle of original known mode by this diesel engine, and in each rotation in two sense of rotation of this axle all with bent axle run-in synchronism.Control Shaft 2 can be fully with respect to the bent axle counter-rotating, that is to say that just walking around when changing, Control Shaft 2 synchronously is rotated further with bent axle then fully with an angular turn opposite with respect to bent axle when just turning to the counter-rotating conversion or from counter steer.Therefore Control Shaft 2 is different when reversing when just changeing with respect to the phase place of bent axle.The counter-rotating of The whole control axle itself is known a kind of measure, is not therefore just described in detail here.For example a counter-rotating servomotor can be set in Control Shaft mechanism, and this mechanism design mode is similar to the mode of describing among German patent DE-A-3128332 that is used for the fuel cam.Therefore because enough spaces are arranged in Control Shaft mechanism, design counter-rotating servomotor is no problem by this way, is enough by the moment of torsion of its generation for the counter-rotating of The whole control axle 2 promptly.
Control Shaft 2 is provided with one and is used to control fuel cam 4 in the firing chamber of a cylinder (not shown) that fuel sprays into a diesel engine and one and is used to control a valve 5 on same cylinder, for example valve cam 3 of an outlet valve 5.Fuel cam 4 activates for example fuel-injection pump (not shown), this pump deliver to fuel in the nozzle in original known mode or the nozzle of cylinder in.
Valve cam 3 activates an elevator pump 7 by a loose roll 6, and its working piston 71 is guided in the sleeve 74 and defines a working space 72.Working space 72 is connected so that hydraulically activate this outlet valve with outlet valve 5 via a hydraulic tubing 8.In the compression movement of the working piston 71 of elevator pump 7-according to diagram promptly one make progress move-hydraulic medium in hydraulic tubing 8 is placed under the pressure, is opened by this pressure exhaust valve 5.Valve cam 3 is being controlled the unlatching of outlet valve 5 by this way.
According to the present invention, a kind of device that is different from valve cam 3 is provided to closing of control valve 5.These devices comprise that overflows a connecting passage 73 in first one exemplary embodiment, and it is arranged on the release of pressure that is used for hydraulic tubing 8 in the elevator pump.Overflow an annular groove 75 on connecting passage leads to working piston 71 from the working space 72 of elevator pump 7 the outer surface.At least be provided with a hole 76 on sleeve 74, this hole feeds the annular pass 77 around sleeve 74 outer walls.Annular pass 77 is connected to an outlet passage 78, and by this passage hydraulic medium, for example a kind of oil can flow out.On the one hand the annular groove 75 on working piston 71 walls and on the other hand the one or more holes 76 on sleeve 74 be positioned to mutual a kind of like this mode that becomes, promptly only they just are interconnected when working piston 71 is positioned at its upper dead center regional.So-called upper dead center is exactly the reversing point of working piston 71, at this moment the volume minimum of working space 72.
The device that control valve 5 is closed in first one exemplary embodiment also comprises a restrictor device, for example, a throttle valve 9, outlet passage 78 leads to this valve.Throttle valve 9 is used to regulate the release of pressure of hydraulic tubing 8.Article one, return passage 10 extends supply line 11 that is used for hydraulic medium of feeding from throttle valve 9.Supply line 11 leads to hydraulic tubing 8 from a hydraulic medium supply container (not shown) by a safety check 12.
It is fixed that fuel cam 4 and valve cam 3 all are mounted to respect to Control Shaft 2.Valve cam 3 is settled in such a way and is designed, i.e. the unlatching of this valve is taking place with respect to the certain crank angle displacement of fuel injection, and this is identical to the rotation on the both direction of Control Shaft 2 basically.Fig. 3 shows the cross-sectional view of such valve cam 3.The profile of valve cam 3 comprises one first side 31 and one second side 32.Valve cam 3 has an intermediate portion 34 between two sides 31,31, and its profile is arranged essentially parallel to basic circle 33 extensions in this position.Because this intermediate portion, the profile of valve cam 3 has two effective summit S1 and S2, and each summit wherein is all in the intermediate location between the intermediate location between first side 31 and intermediate portion 34 and the intermediate portion 34 and second side 32.So-called " effectively summit " is used to refer to a point on valve cam 3 profiles, and when the opening process of valve 5 had just been finished, just loose roll 6 (Fig. 1) just contacted on this aspect when valve 5 is just opened fully.If when loose roll 6 was positioned on the effective summit, the working piston 71 of elevator pump 7 roughly was in its top dead center.
Valve cam 3 designs in such a way, promptly two effective summit S1 and S2 should be positioned to no matter the direction of rotating why this corresponding first effective summit S1 or S2 in the same angle of sense of rotation top offset with respect to the summit of fuel cam 4.This meaning is these two effective summit S1 and S2 angle that is substantially equal to commutation angle of displacement each other for example, and in other words, the length of intermediate portion 34 is equivalent to the angle that commutates basically.
Working method of apparatus of the present invention 1 or method of the present invention are illustrated with reference to Fig. 2 below.Here will finish crank angle KW35 ° the time the latest with the injection of the character imagination fuel oil of demonstration.The actuator that is to say petrolift when crank angle KW is 35 ° arrives upper dead center position.The unlatching of outlet valve 5 takes place when crank angle KW is 180 °.According to the custom term, crank angle KW is meant position of piston in cylinder of internal-combustion engine.Usually when piston is positioned at its upper dead center crank angle KW=0 °, and when piston is positioned at its lower dead centre KW=180 °.
Chart among Fig. 2 makes the arrangement of cam 3,4 on Control Shaft 2 clearly illustrate out with the chart of linearization.The crank angle KW that aligns commentaries on classics mark and draw on the V axle to the then plotting of counter-rotating on the R axle.The summit of fuel cam 4 all is positioned at KW=35 ° to both direction.The commutation angle that Control Shaft turns over when the direction of rotating changes is substantially equal to the twice of the summit of fuel cam 4 from the angular distance of the upper dead center (KW=0 °) of piston, just, in this concrete example, be 70 ° (an extra delay might be provided thus).
First effective summit S1 of valve cam 3 is positioned at KW=180 ° thereby it between the positive refunding to have an angular distance d1 to fuel cam 4 summits be 145 ° of KW.The intermediate portion 34 of valve cam has a length d 2, and this length is equivalent to 70 ° of KW, just is equivalent to commutation angle.The result is that the second effective summit S2 that aligns commentaries on classics is positioned at KW=250 °.It on positive veer (V axle) reach 145 ° to the angular distance d3 of fuel cam 4.
Just changeing in service, at first carrying out by the fuel injection of fuel cam 4 (its summit is positioned at KW=35 °) control.When Control Shaft 2 is rotated further, loose roll 6 (Fig. 1) will be run into first side 31 of valve cam 3, and the working piston 71 of elevator pump 7 moves up (as shown in Figure 1) thus.Along with the stroke movement increase of working piston 71, the pressure in the hydraulic tubing 8 also rise, thereby the unlatching of valve 5 also just begins.When loose roll 6 arrived first effective summit S1 (KW=180 °), outlet valve 5 is the working piston 71 of elevator pump 7 position at dead point thereon of ascending the throne with regard to being opened fully.Being connected thereupon between annular groove 75 and the hole 76 connected, thereby hydraulic medium can be from working space 72 via overflow connecting passage 73, annular groove 75, and hole 76, annular pass 77 and outlet passage 78 flow out.The result is that the pressure in the hydraulic tubing 8 descends (release of pressure), thereby valve 5 is closed.By calibration or regulate throttle valve 9, and closed procedure or shut-in time point just can be influenced in the mode of controlling or be controlled.The hydraulic medium that flows out from throttle valve 9 enters supply line 11 by return passage 10.Like this, closing by the release of pressure in the hydraulic tubing 8 of valve 5 realizes, and the working piston 71 of elevator pump 7 remains on its upper dead center position in the down periods of valve 5 by valve cam 3, this means that loose roll 6 passes through on the intermediate portion 34 of valve cam 3.After loose roll 6 rolls across the second summit S2, working piston 71 for example loads (itself being known) by a spring (not shown) and promptly moves down as shown in fig. 1, thus, on the one hand overflow connecting passage 73 is closed and hydraulic medium enters in the hydraulic tubing 8 with regard to being sucked out from supply line 11 at once when making the degree that safety check 12 opens when the pressure in the hydraulic tubing 8 is reduced on the other hand.When Control Shaft 2 was rotated further, fuel injection was just carried out in the mode that is subjected to 4 controls of fuel cam again then, and its summit reaches KW=395 °, is equivalent to KW=35 °.
For running backward (the axle R among Fig. 2), Control Shaft 2 at first entirely rotates a commutation angle with respect to bent axle, is exactly 70 ° in this concrete example.The result is that the summit of fuel cam arrives crank angle KW=35 ° again.Loose roll 6 just bumps on second side 32 of valve cam 3 when Control Shaft 2 is rotated further, and thus, with noted earlier the same, valve 5 just is opened.When the second effective summit S2 that is positioned at valve cam 3 when loose roll 6 goes up (KW=180 °), valve 5 just is opened fully.Closed running is similar with running forward then.
Therefore, first side 31 of valve cam 3 is used for control valve 5 when turning round forward unlatching second side 32 then is used in opposite running, and in the both direction that rotates, closing of valve 5 is to use the other device control that is different from valve cam 3, and the step-down or the release of pressure of hydraulic tubing 8 takes place by this device.Because being used for valve is controlled at one of them side 31 or 32 of only requiring valve cam 3 on each sense of rotation, so two sides 31,32 can be drawn back, thereby it is irrelevant with the sense of rotation of Control Shaft 2 with angular distance d1 separately or the d2 (crank angle is poor) of each effective summit S1 or S2 to be in the top fuel cam 4 of sense of rotation.Though therefore for diesel engine be to turn round forward or backward all to guarantee best service behaviour, particularly all the more so with regard to the cooperation between the actuating of fuel injection and valve.
Fig. 4 illustrates the sectional view of a variant of valve cam 3 structures.Two have the effect of work summit S1 in this variant, and the profile of the valve cam between the S2 is just also different with basic circle at the place, intermediate portion, is not parallel with basic circle 33, but a least part is arranged.By this measure, can reduce in order to the amount of the hydraulic medium that must flow out of cut-off valve 5.By this least part, the working piston 71 (Fig. 1) of elevator pump 7 only needs to move down a little (as shown in the figure).Yet this amplitude that moves is so little, thereby still is in its upper dead center position at 5 down periods of valve working piston 71, thereby hydraulic medium can flow out via overflow connecting passage 73.
Clearly, fuel cam 4 and/or valve cam 3 might not be positioned to symmetry.Two sides 31,32 of valve cam 3 also can be different naturally, and are for example different on steepness and/or length.Two sides for fuel cam 4 also are the same.
Fig. 5 illustrates second one exemplary embodiment of the present invention with the symbol explanation.With the main difference place of first one exemplary embodiment be device about closed valve 5.In others, the explanation of the first exemplary real row is applicable to second one exemplary embodiment too.Being provided with one in second one exemplary embodiment is too activated by valve cam 3 and is connected to elevator pump 7 ' on the valve 5 so that activated valve 5 via hydraulic tubing 8.The device of closing of control valve 5 comprises one by electricity or electronically controlled valve 20, is used for the release of pressure of hydraulic tubing 8.Electric or electronically controlled valve 20 can be directly actuated or pre-control.
Hydraulic tubing 8 leads to electromechanical valve 20 from elevator pump 7 ' and leads to outlet valve 5 then therefrom again.In Fig. 5 with symbolism the position of the valve 20 that illustrates, elevator pump 7 ' is connected to outlet valve 5, thereby will make outlet valve 5 open once reaching enough pressure when hydraulic medium.For closing outlet valve 5, valve 20 is placed on the right part position of the symbolic valve 20 that shows, that part of hydraulic tubing 8 that leads to outlet valve 5 from the outlet of valve 20 is connected on the return passage 10 in other words, thereby hydraulic medium can flow out from the hydraulic tubing 8 of described part by return passage 10 in controlled mode.Form the release of pressure of outlet valve 5 thereupon and close.Return passage 10 can or be connected on the supply line 11 of hydraulic medium or directly is connected on the supply container 13 of hydraulic medium.The actuating of valve 20 can be finished by control impuls, and this pulse arrives valve 20 from a control unit 60 via signaling line 50.For closing of outlet valve 5 occurred on the desirable time point, just, on the desirable crank angle KW, a measuring equipment is set up, so that measure the position, angle of Control Shaft 2.Measuring equipment comprises for example angle transducer 30, and this sensor is connected on the control unit 60 by a signal line 40.When control unit 60 must be closed according to the acquisition of signal exhaust valve 5 that sends from angle transducer 30, it just produced a control impuls at once, and this pulse excites the corresponding actuating of valve 20 by signaling line 50.Opening also of outlet valve 5 controlled by valve cam 3 in this second one exemplary embodiment, and the setting of electricity or electronically controlled valve 20 is to be used for controlling closing of outlet valve 5.Certainly other measuring equipment also can be used for producing a signal, can confirm that according to this signaling control unit 60 closing of outlet valve 5 must execution.For example, noncontacting proximity sensor, position transducer, inductive sensor, photodiode or similar device can be provided with, and for example can detect the position of the working piston 71 of elevator pump 7 ' or the position, angle of valve cam 3 by this.
By the invention provides the apparatus and method of the valve control that is used for the reversible diesel machine, this apparatus and method see that from the viewpoint that is provided with and construct being is economical especially simply thereby also, therein, Control Shaft, cam and all design compactly especially around their shell, thereby can save the space, all admit of desirable ride quality to turning round forward and backward in addition.
Device of the present invention and method of the present invention are particularly suitable for reversible two-stroke large-scale diesel engine, as used the sort of in shipbuilding industry.
Claims (18)
1. be used for the device that valve is controlled in a reversible diesel machine, this device comprises that one can be reversed and rotary Control Shaft (2) on both direction, Control Shaft is provided with at least one fuel cam (4), be used to control the injection of fuel oil, with at least one valve cam (3), be used to control a valve (5) of diesel engine, this valve cam (3) is being controlled the unlatching of valve (5), it is characterized in that, also be provided with the other device that is different from valve cam (3) of closing in order to control valve (5), described fuel cam (4) and valve cam (3) all are mounted to respect to Control Shaft (2) has fixing position, wherein valve cam (3) is installed by this way and is designed, the unlatching that is valve (5) is taking place with respect to (KW) displacement of the certain crank angle of fuel injection, and this rotation to the both direction of Control Shaft (2) all is identical basically.
2. device as claimed in claim 1, it is characterized in that, have two effective summit (S1 on the profile of valve cam (3), S2), settle by this way on these two summits, promptly no matter the direction of rotating why, first summit of valve cam (3) (S1 or S2) all is the identical angle of top displacement with respect to fuel cam (4) in each case on corresponding sense of rotation.
3. device as claimed in claim 2 is characterized in that, wherein effective summit (S1 of valve cam (3), S2) one of displacement be substantially equal to the to commutate angle of angle each other, in addition, (S1, S2) profile of the valve cam between (3) and basic circle (33) is different on two effective summits.
4. device as claimed in claim 1, it is characterized in that, wherein also be provided with an elevator pump (7) that activates by valve cam, this pump is connected on the valve (5) by a hydraulic tubing (8), so that activate this valve (5), wherein control valve (5) device of closing comprises an overflow connecting passage (73) that is arranged in the elevator pump (7), is used for the release of pressure of hydraulic tubing (8).
5. device as claimed in claim 4 is characterized in that, wherein the device of closing of control valve (5) comprises a restrictor device (9), in order to regulate the release of pressure of hydraulic tubing (8).
6. as each described device in the claim 1 to 3, it is characterized in that, wherein being provided with one is activated by valve cam and is connected elevator pump (7 ') on the valve (5) by a hydraulic tubing (8), so that hydraulically activate this valve (5), wherein the device of closing of control valve (5) comprises an electricity or electronically controlled valve (20), is used for the release of pressure of hydraulic tubing (8).
7. be used for the method that valve is controlled in a reversible diesel machine, comprise the steps: in this internal-combustion engine, to be provided with a Control Shaft that can on both direction, rotate (2), at least one fuel cam (4) is set on axle is used to control the injection of fuel oil and the valve (5) that at least one valve cam (3) is used to control diesel engine, make this diesel engine rotate with first operator scheme and in second operator scheme, be rotated with the commutation operation along a direction, unlatching by valve cam (3) control valve (5), it is characterized in that, by being different from other device the closing of control valve (5) of valve cam (3), described fuel cam (4) and valve cam (3) all are mounted to respect to Control Shaft (2) has fixing position, wherein valve cam (3) is installed by this way and is designed, the unlatching that is valve (5) is taking place with respect to (KW) displacement of the certain crank angle of fuel injection, and this rotation to the both direction of Control Shaft (2) all is identical basically.
8. method as claimed in claim 7 is characterized in that, wherein valve (5) is by an elevator pump (7; 7 ') hydraulically open, this elevator pump activated by valve cam (3) and wherein valve (5) close by release of pressure, at valve (5) down periods elevator pump (7; 7 ') working piston (71) is remained on the position of its upper dead center by valve cam (3).
9. reversible diesel machine, the device that is used for valve control in this diesel engine comprises that one can be reversed and rotary Control Shaft (2) on both direction, Control Shaft is provided with at least one fuel cam (4), be used to control the injection of fuel oil, with at least one valve cam (3), be used to control a valve (5) of diesel engine, this valve cam (3) is being controlled the unlatching of valve (5), it is characterized in that, also be provided with the other device that is different from valve cam (3) of closing in order to control valve (5), described fuel cam (4) and valve cam (3) all are mounted to respect to Control Shaft (2) has fixing position, wherein valve cam (3) is installed by this way and is designed, the unlatching that is valve (5) is taking place with respect to (KW) displacement of the certain crank angle of fuel injection, and this rotation to the both direction of Control Shaft (2) all is identical basically.
10. reversible diesel machine as claimed in claim 9, it is characterized in that, have two effective summit (S1 on the profile of valve cam (3), S2), settle by this way on these two summits, promptly no matter the direction of rotating why, first summit of valve cam (3) (S1 or S2) all is the identical angle of top displacement with respect to fuel cam (4) in each case on corresponding sense of rotation.
11. reversible diesel machine as claimed in claim 10, it is characterized in that, effective summit (S1 of valve cam (3) wherein, S2) one of displacement be substantially equal to the to commutate angle of angle each other, in addition, (S1, S2) profile of the valve cam between (3) and basic circle (33) is different on two effective summits.
12. reversible diesel machine as claimed in claim 9, it is characterized in that, wherein also be provided with an elevator pump (7) that activates by valve cam, this pump is connected on the valve (5) by a hydraulic tubing (8), so that activate this valve (5), wherein control valve (5) device of closing comprises an overflow connecting passage (73) that is arranged in the elevator pump (7), is used for the release of pressure of hydraulic tubing (8).
13. reversible diesel machine as claimed in claim 12 is characterized in that, wherein the device of closing of control valve (5) comprises a restrictor device (9), in order to regulate the release of pressure of hydraulic tubing (8).
14. as each described reversible diesel machine in the claim 9 to 11, it is characterized in that, wherein being provided with one is activated by valve cam and is connected elevator pump (7 ') on the valve (5) by a hydraulic tubing (8), so that hydraulically activate this valve (5), wherein the device of closing of control valve (5) comprises an electricity or electronically controlled valve (20), is used for the release of pressure of hydraulic tubing (8).
15. reversible diesel machine as claimed in claim 9 is characterized in that, this diesel engine is the two-stroke large-scale diesel engine.
16. the operation method of a reversible diesel machine, comprise the steps: in this internal-combustion engine, to be provided with a Control Shaft that can on both direction, rotate (2), at least one fuel cam (4) is set on axle is used to control the injection of fuel oil and the valve (5) that at least one valve cam (3) is used to control diesel engine, make this diesel engine rotate with first operator scheme and in second operator scheme, be rotated with the commutation operation along a direction, unlatching by valve cam (3) control valve (5), it is characterized in that, by being different from other device the closing of control valve (5) of valve cam (3), described fuel cam (4) and valve cam (3) all are mounted to respect to Control Shaft (2) has fixing position, wherein valve cam (3) is installed by this way and is designed, the unlatching that is valve (5) is taking place with respect to (KW) displacement of the certain crank angle of fuel injection, and this rotation to the both direction of Control Shaft (2) all is identical basically.
17. method as claimed in claim 16 is characterized in that, wherein valve (5) is by an elevator pump (7; 7 ') hydraulically open, this elevator pump activated by valve cam (3) and wherein valve (5) close by release of pressure, at valve (5) down periods elevator pump (7; 7 ') working piston (71) is remained on the position of its upper dead center by valve cam (3).
18. method as claimed in claim 16 is characterized in that, this diesel engine is the two-stroke large-scale diesel engine.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP97810766A EP0909883B1 (en) | 1997-10-14 | 1997-10-14 | Arrangement and method for valve driving in a reversible diesel engine |
| EP97810766.2 | 1997-10-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1214408A CN1214408A (en) | 1999-04-21 |
| CN1247881C true CN1247881C (en) | 2006-03-29 |
Family
ID=8230426
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB981213561A Expired - Fee Related CN1247881C (en) | 1997-10-14 | 1998-10-13 | Arrangement and method for valve control of reversible diesel combustion engine |
Country Status (8)
| Country | Link |
|---|---|
| EP (1) | EP0909883B1 (en) |
| JP (1) | JPH11159314A (en) |
| KR (1) | KR100527820B1 (en) |
| CN (1) | CN1247881C (en) |
| DE (1) | DE59708956D1 (en) |
| DK (1) | DK0909883T3 (en) |
| PL (1) | PL329104A1 (en) |
| TW (1) | TW360739B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101415936B (en) * | 2006-04-12 | 2011-07-27 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Crosshead type large-sized uniflow type two-stroke diesel motor |
Families Citing this family (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE59708956D1 (en) * | 1997-10-14 | 2003-01-23 | Waertsilae Schweiz Ag Winterth | Arrangement and method for valve control of a reversible diesel internal combustion engine |
| DE10155669A1 (en) * | 2001-11-13 | 2003-05-22 | Bosch Gmbh Robert | Device for controlling at least one gas exchange valve |
| CN102251895B (en) * | 2006-04-12 | 2013-03-27 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Crosshead-shaped large uniflow-type dual-stroke diesel engine |
| JP2008248838A (en) * | 2007-03-30 | 2008-10-16 | Man Diesel As | Cam driven exhaust valve operation system for large size two cycle diesel engine |
| US8033954B2 (en) * | 2007-04-18 | 2011-10-11 | GM Global Technology Operations LLC | Hybrid powertrain with reversing engine and method of control |
| CN101509404B (en) * | 2008-02-15 | 2011-05-18 | 蔡学功 | Variable valve system |
| JP5015975B2 (en) * | 2009-02-04 | 2012-09-05 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Cam-driven exhaust valve actuation system for large two-cycle diesel engines |
| JP5189069B2 (en) * | 2009-12-17 | 2013-04-24 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Cam-driven exhaust valve actuation system for large two-cycle diesel engines |
| RU2536651C1 (en) * | 2013-12-16 | 2014-12-27 | Анатолий Александрович Рыбаков | Reversing method of internal combustion engine with reversing starter and actuating mechanism of gas distributing valve and fuel injector with charging of its pneumatic accumulator by compressed air |
| RU2544117C1 (en) * | 2013-12-16 | 2015-03-10 | Анатолий Александрович Рыбаков | Method of engine shaft rotation reversal |
| RU2543907C1 (en) * | 2013-12-16 | 2015-03-10 | Анатолий Александрович Рыбаков | Method of engine shaft rotation reversal |
| RU2544121C1 (en) * | 2013-12-16 | 2015-03-10 | Анатолий Александрович Рыбаков | Method of engine shaft rotation reversal |
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| RU2566860C1 (en) * | 2014-10-07 | 2015-10-27 | Анатолий Александрович Рыбаков | Ice crankshaft reversing by gas pressure control valve pneumatic drive system with pneumatic accumulator charging with gas from compensating pneumatic accumulator and fuel injector control system |
| RU2576771C1 (en) * | 2015-01-29 | 2016-03-10 | Анатолий Александрович Рыбаков | Method for reversal internal combustion engine with reverse starter mechanism and pneumatic actuator system of three-valve gas distributor with charging of accumulator of system by atmospheric air |
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| RU2594829C1 (en) * | 2015-02-05 | 2016-08-20 | Анатолий Александрович Рыбаков | Method for reversing internal combustion engine by reversing starter mechanism and pneumatic drive system of two-valve gas distributor, with charging pneumatic accumulator system using gas from compensating pneumatic accumulator |
| RU2576696C1 (en) * | 2015-02-05 | 2016-03-10 | Анатолий Александрович Рыбаков | Method for reversal internal combustion engine with reverse starter mechanism and pneumatic actuator system of two-valve gas distributor with charging of accumulator of system by atmospheric air |
| RU2576699C1 (en) * | 2015-02-05 | 2016-03-10 | Анатолий Александрович Рыбаков | Method for reversal of internal combustion engine with reverse starter mechanism and pneumatic actuator system of two-valve gas distributor with charging of pneumatic accumulator of system with gas from compensation pneumatic accumulator |
| RU2578934C1 (en) * | 2015-02-19 | 2016-03-27 | Анатолий Александрович Рыбаков | Method for reversal of internal combustion engine with starter mechanism and pneumatic actuator system of three-valve gas distributor with charging of accumulator of system by atmospheric air |
| RU2581968C1 (en) * | 2015-02-19 | 2016-04-20 | Анатолий Александрович Рыбаков | Method for reversal of internal combustion engine with reverse starter mechanism and pneumatic actuator system of three-valve gas distributor with charging of pneumatic accumulator of system with gas from compensation pneumatic accumulator |
| RU2591364C1 (en) * | 2015-02-19 | 2016-07-20 | Анатолий Александрович Рыбаков | Method of reversing internal combustion engine by starter mechanism and system of pneumatic drive of two-valve gas distributor with charging of its system air accumulator by atmospheric air |
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| GB991388A (en) * | 1962-07-11 | 1965-05-05 | Stork Koninklijke Maschf | Reversible two-stroke internal combustion engine with cam-controlled exhaust and fuel supply members |
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| DE3128332A1 (en) | 1981-07-14 | 1983-01-27 | Gebrüder Sulzer AG, 8401 Winterthur | "CAM SHAFT CONTROL SHAFT" |
| JPH07116928B2 (en) * | 1986-09-10 | 1995-12-18 | 石川島播磨重工業株式会社 | Cam device for internal combustion engine |
| DE59708956D1 (en) * | 1997-10-14 | 2003-01-23 | Waertsilae Schweiz Ag Winterth | Arrangement and method for valve control of a reversible diesel internal combustion engine |
| KR100991388B1 (en) * | 2008-04-08 | 2010-11-03 | 주식회사 비즈모델라인 | Method for Operating Intelligent Smart Card |
| JP6003886B2 (en) * | 2011-05-13 | 2016-10-05 | 三菱化学株式会社 | Non-aqueous secondary battery carbon material, negative electrode using the carbon material, and non-aqueous secondary battery |
-
1997
- 1997-10-14 DE DE59708956T patent/DE59708956D1/en not_active Expired - Lifetime
- 1997-10-14 EP EP97810766A patent/EP0909883B1/en not_active Expired - Lifetime
- 1997-10-14 DK DK97810766T patent/DK0909883T3/en active
-
1998
- 1998-02-11 TW TW087101840A patent/TW360739B/en not_active IP Right Cessation
- 1998-08-20 JP JP10234228A patent/JPH11159314A/en active Pending
- 1998-10-09 PL PL98329104A patent/PL329104A1/en unknown
- 1998-10-13 CN CNB981213561A patent/CN1247881C/en not_active Expired - Fee Related
- 1998-10-13 KR KR1019980042753A patent/KR100527820B1/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101415936B (en) * | 2006-04-12 | 2011-07-27 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Crosshead type large-sized uniflow type two-stroke diesel motor |
Also Published As
| Publication number | Publication date |
|---|---|
| PL329104A1 (en) | 1999-04-26 |
| JPH11159314A (en) | 1999-06-15 |
| DK0909883T3 (en) | 2003-01-06 |
| TW360739B (en) | 1999-06-11 |
| DE59708956D1 (en) | 2003-01-23 |
| KR100527820B1 (en) | 2006-03-23 |
| EP0909883A1 (en) | 1999-04-21 |
| KR19990037055A (en) | 1999-05-25 |
| CN1214408A (en) | 1999-04-21 |
| EP0909883B1 (en) | 2002-12-11 |
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